US5829407A - Internal combustion engines - Google Patents

Internal combustion engines Download PDF

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Publication number
US5829407A
US5829407A US08/875,355 US87535597A US5829407A US 5829407 A US5829407 A US 5829407A US 87535597 A US87535597 A US 87535597A US 5829407 A US5829407 A US 5829407A
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Prior art keywords
combustion chamber
fuel
engine
air
delivery
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US08/875,355
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English (en)
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Stephen James Watson
Darren Andrew Smith
Robert Walter Frew
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Delphi Technologies Inc
Delphi Automotive Systems LLC
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Orbital Engine Co Australia Pty Ltd
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Assigned to ORBITAL ENGINE COMPANY (AUSTRALIA) PTY LIMITED reassignment ORBITAL ENGINE COMPANY (AUSTRALIA) PTY LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SMITH, DARREN A., FREW, ROBERT W., WATSON, STEPHEN J.
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Assigned to DELPHI AUTOMOTIVE SYSTEMS LLC reassignment DELPHI AUTOMOTIVE SYSTEMS LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ORBITAL ENGINE COMPANY (AUSTRALIA) PTY. LTD
Assigned to DELPHI TECHNOLOGIES, INC. reassignment DELPHI TECHNOLOGIES, INC. CORRECTION OF THE NATURE OF CONVEYANCE FROM "ASSIGNMENT" TO "LICENSE" Assignors: ORBITAL ENGINE COMPANY (AUSTRALIA) PTY. LTD.
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/12—Engines characterised by precombustion chambers with positive ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
    • F02B19/1004—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder details of combustion chamber, e.g. mounting arrangements
    • F02B19/1014—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder details of combustion chamber, e.g. mounting arrangements design parameters, e.g. volume, torch passage cross sectional area, length, orientation, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to the combustion process of an internal combustion engine and particularly to the enhancement of that process to reduce the level of exhaust emissions, improve the fuel consumption and/or improve combustion stability and/or otherwise enhance the combustion process. More particularly, the invention relates to internal combustion engines wherein fuel is directly injected into the cylinders of the engine.
  • the distribution of fuel within the air charge in the engine combustion chamber is preferably of a stratified nature in order to provide improved fuel consumption.
  • the creation of such a stratified fuel distribution is particularly difficult to achieve where the fuel is introduced into the air charge prior to the air charge entering the combustion chamber. This is particularly so as the fuel must be delivered into the air charge at a specific time related to the engine cycle which will ensure that all of the fuel reaches the combustion chamber before the inlet port associated therewith is closed.
  • the fuel there is a substantial time interval for the fuel to disperse in the air charge, both in the air intake system and in the combustion chamber, before and after closing of the inlet port; and prior to ignition of the air/fuel mixture.
  • Hydrogen is typically a preferred enhancing substance to be used in this procedure, but, due to its high rate of dispersion, (approximately 10 times faster than oxygen), relatively large quantities of hydrogen are usually required, particularly where the fuel and hydrogen are introduced into the air charge prior to the delivery thereof to the combustion chamber. Also, as it is desirable for practical reasons to produce the hydrogen within the vehicle rather than merely to supply a reservoir of pre-produced hydrogen, the resulting large consumption of hydrogen necessitates a substantial "on-board" hydrogen generating capacity which consumes energy, occupies space in, and adds weight to, the vehicle.
  • the physical controls include pockets or cavities formed in the cylinder head at a location relative to the incoming fuel charge to trap therein a readily ignitable fuel/air mixture.
  • pockets or cavities can be in the form of pre-combustion chambers having an igniter device such as a spark plug positioned therein.
  • the effective operation of pre-combustion chambers relies upon the correct readily ignitable fuel/air mixture being established therein, and this can be difficult in an engine wherein the fuel is delivered into the combustion chamber in, or at the same location as, the air charge.
  • the difficulties may arise from the general lack of quiescence within the combustion chamber due to the tumbling or swirling motion of the air or air/fuel mixture prior to ignition.
  • the movement of combustion gases within the combustion chamber after ignition adds to the difficulty in creating a readily ignitable air/fuel mixture at the spark plug.
  • residual gases and contaminants from the previous combustion event within the cylinder cause difficulties as such gases and contaminants are difficult to scavenge or purge from known pre-combustion chambers.
  • an internal combustion engine having a combustion chamber, a pre-combustion chamber communicating with the combustion chamber, injection means located and arranged to periodically deliver controlled amounts of fuel and air into said pre-combustion chamber in a manner and orientation to direct a fuel spray to pass through the pre-combustion chamber into the combustion chamber, and ignition means positioned relative to the pre-combustion chamber and operably arranged to ignite the fuel spray.
  • the engine is of reciprocating type and further includes a cylinder with the cylinder head and a piston defining the combustion chamber.
  • the pre-combustion chamber is preferably formed in the cylinder head.
  • the invention is equally applicable to rotary engines having no cylinders.
  • the injection means is arranged and controlled to deliver a metered quantity of fuel whilst also delivering a quantity of air, not necessarily directly related to the quantity of fuel delivered, each cycle.
  • the period of delivery of air is continued after completion of the delivery of the fuel to assist in the conveying of fuel on a path to pass the ignition means, and may commence prior to, during and/or after the delivery of the fuel.
  • the pre-combustion chamber may be configured to act as a holding chamber for the ignition means.
  • separate fuel and air injectors may deliver directly into the pre-combustion chamber and the control of the timing of the delivery thereof may determine the nature of the fuel spray entering the main combustion chamber.
  • the period of delivery is of a duration and/or timing to purge the pre-combustion chamber such that an ignitable range of air/fuel ratio is established within the vicinity of the ignition means at the time of ignition.
  • the period of delivery is of a duration and/or timing to purge the pre-combustion chamber substantially completely free of fuel and other materials, after each fuel delivery.
  • This purging is in respect of unburnt fuel from the previous cycle, residual combustion gases from the previous combustion event, and the normal air charge for the current cycle which may include recycled or residual exhaust gas.
  • This purging of the pre-combustion chamber following each fuel delivery serves to create a desirable level of quiescence within the pre-combustion chamber and, in particular, at or adjacent the ignition means. Together with a desired air/fuel ratio at the ignition means--which is typically a lean mixture in the trailing portion of the fuel spray--this purging of the pre-combustion chamber contributes to the creation of a reliable and reproducible condition or environment for ignition. Accordingly, the purging contributes substantially to the effective combustion of the fuel and a resultant reduction in the level of emissions.
  • the combustion chamber may be placed in communication with the pre-combustion chamber through a gas conduction means extending from the combustion chamber to the vicinity of the ignition means.
  • the gas conduction means may take any desired form but it may be found convenient to employ a narrow bore conduit extending between the combustion chamber and the pre-combustion chamber.
  • the conduit provides air to the vicinity of the ignition means.
  • the gas conduction means may assist in the formation of a leaner air/fuel mixture during the trailing portion of the fuel spray as this is formed, as a rule, as the piston rises in an engine cylinder causing a flow of gas through the gas conduction means toward the ignition means. A consequence is the formation of a leaner air/fuel mixture in the vicinity of the ignition means.
  • the gas conduction means may be made selectively communicable between the combustion and pre-combustion chambers by a valve means or like device which only allows gas flow therethrough at desired times during an operating cycle of the engine.
  • the pre-combustion chamber is located in the apex region of a cylinder head cavity of wedge shape forming an upper portion of the combustion chamber.
  • a cylinder head cavity of wedge shape forming an upper portion of the combustion chamber.
  • Such a configuration is commonly referred to as a "pent-roofed" combustion chamber and has been used in four valve per cylinder four-stroke cycle engines.
  • the invention is equally applicable to other cylinder head designs.
  • the pre-combustion chamber is located substantially centrally of the longitudinal extent of the wedge and is conveniently of a generally circular cross-section with the injection means penetrating the wall thereof in the vicinity of the junction of the wall of the pre-combustion chamber and the wall of the combustion chamber.
  • the injection means may be arranged in the uppermost portion of the pre-combustion chamber such that it is located centrally with respect to the vertical motion of the piston.
  • the pre-combustion chamber is of a configuration having a narrowed portion, duct, or throat of reduced cross-section, providing the communication between the pre-combustion chamber and the normal combustion chamber.
  • the ignition means is conveniently located to establish initial ignition of the fuel within the duct, neck or upstream thereof.
  • the ignition means is located centrally in the pre-combustion chamber.
  • the pre-combustion chamber is provided by an insert to the cylinder head which communicates with the combustion chamber at one lower end thereof.
  • the insert preferably has a narrow duct or neck at a lower end communicating with the combustion chamber. The upper end of the insert conveniently communicates with the injection means.
  • the gas conduction means is separate from this narrow duct and may be a passage, conduit, tube or like means also, optionally, forming part of the insert.
  • the separate nature of the gas conduction means from the narrow duct allows the generation of a circulation of gas, at relatively high flow through the gas conduction means, advantageously of smaller flow area than the flow area of the narrow duct that promotes rapid travel of a flame front through the narrow duct into the body of the combustion chamber.
  • the pre-combustion chamber is formed as part of the injection means and advantageously communicates with the combustion chamber via a narrow duct.
  • the narrow duct serves to shield the pre-combustion chamber from the typically turbulent environment within the combustion chamber and further serves to create a narrow penetrating stream of fuel into the combustion chamber.
  • the engine may operate on a four stroke cycle such that at least one inlet and at least one outlet valve are provided on opposing sides of the pre-combustion chamber within the cylinder head.
  • This arrangement serves to shield the ignition means from the air which enters the combustion chamber via the inlet valve and contributes to the creation of a reproducible ignition environment at or adjacent the ignition means.
  • This in turn enables other substances to be introduced to the combustion chamber together with the air and/or air/fuel mixture.
  • Such substances may include substantial levels of exhaust gas desirable for emission control.
  • an internal combustion engine having a combustion chamber, a pre-combustion chamber communicating with the combustion chamber, injection means located and arranged to periodically deliver controlled amounts of fuel and air into said pre-combustion chamber in a manner and orientation to direct a fuel spray to pass through the pre-combustion chamber into the combustion chamber, and ignition means positioned relative to the pre-combustion chamber to ignite the fuel spray, said method comprising controlling the delivery of the fuel and air to the pre-combustion chamber so that said pre-combustion chamber is substantially purged of the pre-existing contents therein, establishing an ignitable fuel-air mixture is in a portion of the fuel spray spaced rearwardly from the leading end thereof.
  • the ignitable fuel-air mixture is established in the trailing portion of the fuel spray.
  • a flow of gas from the combustion chamber to the pre-combustion chamber may be generated during the trailing portion of the fuel spray.
  • gas may be caused to flow through a gas conduction means extending from the combustion chamber to the vicinity of the ignition means. In such a manner, "leaning out" of the mixture prior to ignition may be assisted with benefit in terms of emission control.
  • the engine is of reciprocating type having a cylinder head with the cylinder defining, with the piston, the combustion chamber.
  • the pre-combustion chamber is preferably formed in the cylinder head.
  • rotary engines are also comprehended by the method of the invention.
  • the pre-combustion chamber is located in the apex region of a wedge shaped cylinder head cavity forming an upper portion of the combustion chamber.
  • the pre-combustion chamber is located substantially centrally of the longitudinal extent of the wedge.
  • the pre-combustion chamber is conveniently of a generally circular cross-section with the injection means penetrating the wall thereof in the vicinity of the junction of the wall of the pre-combustion chamber and the wall of the combustion chamber.
  • the injection means is preferably of a known type whereby a metered quantity of fuel is delivered into a quantity of compressed air, and is carried by the air into the combustion chamber.
  • a typical example of such an injection means is disclosed in the applicant's U. S. Pat. No. 4,934,329 which is hereby incorporated herein by reference.
  • This type of injector or injection means can be operated to adjust the timing of the introduction of the fuel into the compressed air relative to the commencement of the delivery of the compressed air or other gas from the injector. This enables the timing of the delivery of the fuel to the combustion chamber to be varied relative to the commencement of the delivery of the compressed air. This enables the period of fuel or air delivery to be varied in accordance with engine operating conditions in order to obtain the desired purging of the pre-combustion chamber and positioning of the fuel spray relative to the ignition means as required.
  • the injection means may be controlled to perform more than one injection event within a single combustion cycle.
  • the injection means may be controlled such that, upon a first opening of a nozzle valve of the injection means, the fuel and air delivered into the pre-combustion chamber purges it free of any residual gases and substantially all of the fuel therein.
  • Such injection may also enable mixing of fuel and air within the combustion chamber to facilitate formation of a "homogeneous" charge rather than a stratified charge where the former is appropriate. This is primarily achieved by the end portion of the injection event being constituted by air only.
  • a second injection event may occur wherein a small quantity of fuel and/or air is injected into the purged pre-combustion chamber to establish a desired air/fuel ratio in the vicinity of the ignition means.
  • the pre-combustion chamber is ideally in a quiescent state and a reliable, reproducible ignition environment is created. This is typically achieved by generating a lean ignitable fuel/air mixture at, or in the vicinity of, the ignition means, again being desirably assisted by the additional flow of gas through the gas conduction means from the combustion chamber to the pre-combustion chamber.
  • the invention disclosed herein is particularly suitable for application to four stroke cycle internal combustion engines but may also be applied to engines operating on other cycles such as the two stroke cycle.
  • FIG. 1 is a representation in section of a portion of an internal combustion engine illustrating the form of the pre-combustion chamber.
  • FIG. 2 is an enlarged view of the cylinder head of the engine shown in FIG. 1.
  • FIG. 3 is a view similar to FIG. 2 of a cylinder head having an alternative shape of combustion chamber and pre-combustion chamber.
  • FIG. 4 is a sectional view along line 4--4 in FIG. 2.
  • FIG. 5 is a sectional view of a fuel injection device assembled to a cylinder head of an engine having a hollow pre-combustion chamber.
  • FIG. 6 is a sectional view of an alternative form of pre-combustion chamber that could be used in the fuel injector device shown in FIG. 5.
  • FIG. 7 is a sectional view illustrating the interaction of a stream of fuel with the piston cavity of a piston in a cylinder of an engine incorporating, or operating in accordance with, the present invention.
  • FIG. 8 is a sectional view, similar to FIG. 7, of a further embodiment of the present invention.
  • FIG. 9 is a sectional view, similar to FIG. 6, of a further embodiment of the present invention.
  • FIG. 10 is a sectional view showing a second alternative form of pre-combustion chamber.
  • FIG. 11 is a part-sectional view of a third alternative form of pre-combustion chamber.
  • the engine cylinder 33 has a head 34 and a piston 32 incorporating a cavity 31 in the crown thereof.
  • the under face of the cylinder head 34 has a cavity 35 which, with the piston 32 and upper face portion of the cylinder 33, defines the combustion chamber 36.
  • the cavity 35 may be of any desirable configuration, for example, the wedge-shaped or "pent-roofed" combustion chamber arrangement as depicted in, and described with reference to, FIGS. 3 and 4.
  • the cavity 35 is not essential to the present invention and may be omitted if desired.
  • a pre-combustion chamber 38 located within the cylinder head 34 is of a generally circular cross-section having an upper domed section 39 and a lower frusto-conical downwardly diverging portion 40 as is more clearly seen in FIG. 2.
  • Extending upwardly from the domed section 39 is a co-axial bore 41, preferably internally threaded to receive a portion of a two fluid fuel injector of known construction as previously referred to in the applicant's U.S. patent application Ser. No. 4,934,329.
  • a sloped bore 42 configured to threadably receive a conventional spark plug (not shown).
  • the relative arrangement of the bore 41 and spark plug is such that the electrodes between which the spark is created are located in the location immediately upstream of or at the junction 43 of, the combustion chamber 36 and the frusto-conical portion 40 of the pre-combustion chamber 38.
  • An inlet valve 44 and an outlet or exhaust valve 45 are located within the cylinder head 34 on opposing sides of the pre-combustion chamber 38.
  • the inlet valve 44 is arranged such that it imparts a tumbling action to the air as it enters the combustion chamber 36.
  • the arrangement as shown in the cylinder head 34, together with the resulting combustion chamber 36 is equally applicable to two stroke cycle engines.
  • the invention is not limited to engines in which air is imparted with a tumbling motion and is equally applicable to other engines including those wherein air is input to the combustion chamber with a swirling motion.
  • the inlet valve 44 opens, air enters the combustion chamber 36 with a tumbling action as it is arranged to pass over the uppermost end of the valve 44.
  • An injection means located within the bore 41 is actuated and injects a penetrating narrow fuel spray into the pre-combustion chamber 38.
  • the penetration and narrowness of the fuel spray may be modified such as to take account of the distance between the cavity 31 and the injection means. This injection event scavenges or purges the pre-combustion chamber 38 of fuel and residual gases from the previous combustion event.
  • the injection means is a two-fluid injector as described hereinbefore such that once all the fuel has been injected, air only flows from the injector means into the pre-combustion chamber 38. This serves to create a level of quiescence within the pre-combustion chamber 38 and further purge a majority of the fuel from within the pre-combustion chamber 38. A desirable air/fuel ratio is subsequently generated at the spark plug creating a reproducible, ignitable environment. This environment is created at the plug independent of events occurring in the combustion chamber 36.
  • formation of the air/fuel mixture within the pre-combustion chamber 38 may be arranged to occur in the compressed gases which enter the pre-combustion chamber 38 after fuel has been purged therefrom but before ignition.
  • the combustion chamber 36 may preferably be designed to facilitate the flow of these compressed gases, which mostly comprise air, into the pre-combustion chamber 38 once the initial purging of fuel and gases therefrom has occurred.
  • FIGS. 3 and 4 depict a modified form of cylinder head which may be used in conjunction with the cylinder 33 and piston 32, as previously referred to in reference to FIGS. 1 and 2, a "pent-roofed" combustion chamber arrangement, as previously mentioned, is shown.
  • FIGS. 3 and 4 depict a modified form of cylinder head which may be used in conjunction with the cylinder 33 and piston 32, as previously referred to in reference to FIGS. 1 and 2, a "pent-roofed" combustion chamber arrangement, as previously mentioned, is shown.
  • like parts in FIGS. 3 and 4 are referenced with the same numbers as used in FIGS. 1 and 2.
  • the pre-combustion chamber 47 shown in FIGS. 3 and 4, is located at the apex of cavity 35 and has an upper portion 48 of generally truncated or conical cross-section, comprising an upwardly extending co-axial bore 41.
  • the lower portion 49 of the pre-combustion chamber 47 is formed substantially coaxial with the upper portion 48.
  • the bore 41 is arranged relative to the shaped bore 42 which is configured to threadably receive a conventional spark plug (not shown) such that the electrodes of the spark plug are located in the location immediately upstream of, or at the junction 50 of, the combustion chamber 36 and the lower portion 49 of the pre-combustion chamber 47.
  • the cavity 35 is defined by two upwardly and oppositely inclined surfaces 51 which meet a line 52 and together define a "pent-roofed" combustion chamber 36 which is commonly used on some four stroke cycle engines.
  • the disposition of the annular bore 41 to receive the fuel injector and the spark plug bore 42 complement each other and together provide the ability to achieve particularly desirable ignition conditions, particularly with the fuel injector preferably being of the two fluid type which delivers fuel entrained in a gas such as air.
  • the pre-combustion chamber 38, 47 can be purged of combustion residue from a previous cycle before the initiation of the combustion of the new air/fuel mixture.
  • the actual ignition of the air/fuel mixture can be controlled, particularly in regard to efficiency of ignition of a part of the fuel spray, which is appropriately delivered relative to the ignition means 63.
  • an injection means 70 where the fuel is delivered entrained in a charge of air, desirably together with flow of gas from the combustion chamber through the gas conduction means 81 to the spark plug may enable the entry of the fuel into the air charge to be controlled to achieve a desired air/fuel ratio in the vicinity of the ignition means or spark plug at the time of occurrence of the spark discharge.
  • the pre-combustion chamber may be asymmetric about a longitudinal axis of symmetry of the combustion chamber 36, as shown in FIG. 10.
  • the ignition means 74 is enabled to project deeply into the pre-combustion chamber 76 without interfering with delivery of fuel and air from the injector 101 and assisting ignition because the ignition means 74 is located in a zone at which the desirable air/flow ratio for ignition will exist due to the purging flow of cylinder gases into the pre-combustion chamber 76 from combustion chamber 36 as the piston rises.
  • a secondary gas conduction means may be communicated between a compressed gas source and the pre-combustion chamber 76 to deliver a flow of compressed gas thereto.
  • the compressed gas source may, without limitation, be a compressed air supply, for example, an air compressor or air compressor circuit. Alternatively, or additionally, the air supply may be that supplying compressed air to the injection means 101, for example an air or air/fuel rail.
  • a conduit may form the secondary gas conduction means and may communicate with the compressed gas source at any desired location.
  • the conduit or other form of secondary gas conduction means discharges gas in the vicinity of the ignition means 74 to enable more effective control over air/fuel ratio in this region.
  • a thin dividing member may be provided to physically isolate the pre-combustion chamber 38, 47 from the cylinder head cavity 35.
  • Such a dividing member may be provided with a small orifice or opening suitably located therein such that communication may only occur between the pre-combustion chamber 38 or 47 and combustion chamber 36 through the orifice. It is envisaged that such a dividing member would further shield the pre-combustion chamber 38 or 47 from the turbulence and other activity within the combustion chamber 36. This may contribute further to achieving a level of quiescence in the pre-combustion chamber 38 or 47.
  • FIG. 5 is a sectional view of an alternative shape of pre-combustion chamber 60 where the delivery passage 61 therefrom is of a restricted flow area to increase the velocity of the fuel/air mixture delivered to the combustion chamber.
  • the fuel and air delivered from a two fluid injector unit which may be of the construction disclosed in the applicant's prior U.S. patent, previously referred to herein, enters the pre-combustion chamber 60 at the end 62 and a spark plug is arranged within the passage 63 in the conventional manner.
  • the spark plug is positioned so that it will effectively ignite the fuel/air mixture.
  • the pre-combustion chamber 60 may be arranged as an insert to a cylinder head of an engine or may in fact be formed as part of an injection means or as an attachment thereto which communicates with the main combustion chamber of the engine cylinders.
  • Such an integral unit may then enable retrofitting of the combined injection means and pre-combustion chamber to existing engines. This may be possible using the existing spark plug bore in the cylinder head.
  • FIG. 6 shows such an arrangement wherein a pre-combustion chamber insert 69, not unlike that shown in FIG. 5, is arranged within a corresponding bore in the cylinder head 34.
  • An injection means 70 comprising a fuel injector 71 and an air injector 72 is axially arranged within an opening 73 of the pre-combustion chamber insert 69.
  • a spark plug 74 is arranged to communicate with a corresponding threaded bore 75 in the insert 69 such that the electrodes thereof lie within the pre-combustion chamber 76 at a lower end thereof.
  • the pre-combustion chamber 76 is approximately 0.2-1.0% of the maximum combustion chamber volume and communicates therewith via a narrowed portion, the duct or throat 77.
  • the throat is arranged to provide a contained and penetrating fuel spray into the combustion chamber 36.
  • the throat 77 is narrow to provide increased velocity to the gases exiting the pre-combustion chamber 76.
  • the throat 77 cannot be too narrow or the time taken to purge the pre-combustion chamber 76 will be too long and subsequently affect the satisfactory operation of the engine.
  • the cross-sectional area of the throat 77 may be approximately 30-50% larger than the nozzle opening (not shown) of the injection means 70 which enables communication with the pre-combustion chamber 76.
  • the small throat area causes the chamber 76 to fill with fuel and air which substantially scavenges or purges the chamber 76 of any residual gases.
  • This fuel/air mixture is subsequently delivered into the main combustion chamber 36 in the form of a narrow penetrating spray which interacts with the cavity 31 in the piston 32 in a known manner (see FIG. 7).
  • the cavity 31 may be arranged with a specific shape such that it interacts with the fuel spray in the desired manner. In the case of the cavity 31, as shown in FIG.
  • the axis of the pre-combustion chamber 76, and consequently the axis of the fuel/air spray emitted from the throat 77, is coincident with the axis of the cavity 31 at a convenient piston position.
  • the two axes are coincident when the piston is at a position corresponding to 55° BTDC.
  • air from the air injector 72 only is delivered by the injection means 70. This serves to further purge substantially all of the fuel from the pre-combustion chamber 76 and create a desirable air/fuel ratio at the spark plug electrodes.
  • the pre-combustion chamber 76 is essentially free of any residual gases and is substantially isolated from the main combustion chamber 36 such that a desirable level of quiescence is created therein. This is a reliable and reproducible environment for ignition.
  • the air fuel ratio at the spark plug electrodes may be controlled to be different to that present in the main combustion chamber 36. This is essentially possible due to the flexibility of the two fluid injection means 70.
  • ignition of the contents of pre-combustion chamber 76 may take place after entry thereto of compressed gases from the combustion chamber 36.
  • compressed air from the combustion chamber 36 flows into the pre-combustion chamber 76 as a result of the increase in pressure in combustion chamber 36 caused by the rise of the piston 32 in the cylinder.
  • gases being mostly air, serve to further lean out the air/fuel mixture in the pre-combustion chamber 76. Accordingly, it may be desirable to ignite the fuel/air mixture as this air enters the pre-combustion chamber 76 rather than when the final portion of air is delivered by injection means 70.
  • the combustion chamber cavity 35 may preferably be arranged to facilitate the flow of combustion gases back into the pre-combustion chamber 76.
  • Such a configuration is shown in FIGS. 6 and 7.
  • the air/fuel mixture in the pre-combustion chamber 76 may be stoichiometric while a large proportion of exhaust gas from an EGR system remains in the combustion chamber 36.
  • a torch of flame is emitted into the combustion chamber 36, through the throat 77, and into the tumbling air within the combustion chamber 36 which results in rapid combustion of the air/fuel mixture therein.
  • the ability to mix/use different substances with the air and fuel such as exhaust gas from a suitable EGR system, such as that disclosed in the applicant's corresponding International patent application No. PCT/AU94/00288, is increased.
  • the air/fuel mixture in the chamber 76 may be stoichiometric while a large proportion of exhaust gas from an EGR system remains in the combustion chamber 36.
  • combustion possible is essentially faster than that which may be achieved by way of a conventional spark plug in the combustion chamber arrangement and may admit reduced fuel consumption and NO x emissions. Further, this construction allows for air/fuel ratios in the main combustion chamber 36 to be as low as 120:1.
  • spark plug 74 and injection means 70 to the pre-combustion chamber 76 are not limited to that shown in FIG. 6 and other variants are possible.
  • both the spark plug 74 and the nozzle opening of the injection means 70 may be arranged at the uppermost end of the chamber 76 in a side by side relationship.
  • the spark plug 74 may be replaced by an ignition means which has electrodes arranged within the insert 69 such that a spark occurs across the throat 77 of the pre-combustion chamber 76.
  • the spark plug 74 or electrodes arranged within the insert 69 may be configured to spark onto the end of the injection means 71 itself or onto a projection 78 of the injection means as seen in FIG. 7.
  • the fuel and air injectors 71 and 72 may be arranged to separately deliver fuel and air into the pre-combustion chamber 76 via separate orifices.
  • Such orifices could be arranged at the top of the pre-combustion chamber 76 and the timing of delivery of both the fuel and air would determine the resultant air/fuel ratio and nature of the fuel spray to be delivered through the throat 77.
  • a plurality of throats 77, or orifices, may be provided through which fuel may be delivered to the combustion chamber 36.
  • the pre-combustion chamber 76 may be provided with a baffle 106, preferably curvilinear to promote desired spray geometry though a vertical plate could be employed.
  • the baffle 106 acts as a flow guide for the fuel/air mixture delivered from injector 101 and here the ignition means 74 is located between baffle 106 and the inner wall of pre-combustion chamber 76 in a region 107 defined therebetween which is isolated from the fuel spray from injector 101.
  • flow of the air/fuel mixture is directed downward toward the narrowed portion or throat 77 and gases in region 107 outward from the baffle 106 remain fuel-lean as the spray from the injector 101 does not reach this region 107.
  • the "leaning-out" of fuel in gases present in region 107 may further be promoted by bleeding of air or other gases from the compressed air or gas source (not shown), for example as described with reference to FIG. 10, through a secondary gas conduction means into region 107.
  • the secondary gas conduction means may be a conduit which opens into the pre-combustion chamber through a small aperture formed in the wall of pre-combustion chamber 76.
  • the conduit may connect with the air or gas supply to the engine.
  • the air or gas supply means may be made selectively communicable, under certain engine operating conditions, with region 107, through a valve, orifice or other flow control means. If a valve is employed, this could be solenoid controlled.
  • the aperture remains continuously open and is small enough to enable flow of gas into the pre-combustion chamber region 107, preferably in the vicinity of the ignition means to enable more effective control over air/fuel ratio in this region.
  • the aperture is small, the quantity of combustion gases which may enter the aperture and thus the conduit or other secondary gas conduction means is insubstantial.
  • the timing of the delivery of the air/fuel mixture by the injector to the pre-combustion chamber of each of the embodiments described, and the activation of the spark plug are typically controlled by an electronic control unit (ECU) as is well known in the engine management field.
  • the ECU is programmed so that the delivery of the air charge to the pre-combustion chamber and the introduction of the fuel to the air charge are timed so that an ignitable mixture is created at the spark plug when the spark is delivered.
  • the timing of the delivery of the spark is preferably such that it does not ignite the leading section of the fuel spray issued during the injection event and preferably ignites the trailing or an outer lean section thereof.
  • FIG. 8 shows an embodiment similar to FIG. 7 described above with the additional feature of a gas conduction means, here taking the form of a conduit 81.
  • the conduit 81 extends from the combustion chamber 36 to the spark plug 74 disposed within the pre-combustion chamber 76.
  • the use of a light metal, a conductive material allows the formation of a heat transfer path as well as a gas flow path from the combustion chamber 36 to the pre-combustion chamber 76.
  • the conduit 81 also forms part of an insert to the cylinder head of the engine though it could equally be formed separately, for example as part of the cylinder block.
  • the conduit 81 extends approximately parallel to an axis extending vertically through the centre of the combustion chamber 36 and cylinder head and opens approximate to spark plug 74.
  • the conduit 81 may be arranged in any desired manner at an any desired trajectory which facilitates manufacture and achieves the objective of delivering gas to the vicinity of spark plug 74 to achieve a desired lean air/fuel mixture thereat in the trailing portion of the fuel injection event.
  • conduit 81 is separate from the throat of the pre-combustion chamber and, advantageously, does not extend therethrough.
  • the throat 77 which serves the important function of direction of fuel spray into the combustion chamber 36 is not obstructed by the conduit 81.
  • conduit 81 should be less than that of throat 77 to ensure that a high pressure flow of air is created therethrough in response to rise of a piston within the cylinder of which combustion chamber 36 forms part.
  • Operation is analogous to that described with respect to FIG. 7 so when the injection means 70 injects the fuel/air mixture into the pre-combustion chamber 76, the chamber 76 fills with fuel and air which substantially scavenges or purges the chamber 76 of any residual gases. To some extent, this may be assisted by vacuum through conduit 81 when the piston descends through the cylinder. After the main portion of injection has taken place, air from the air injector 72 only is delivered by the injection means 70. This serves to further purge substantially all of the fuel from the pre-combustion chamber 76 and helps to create a desirable air/fuel ratio for ignition at the spark plug electrodes.
  • the gas conduit 81 may play a most important role.
  • the expansion that follows ignition causes air flow through the throat 77 and a kind of circulation may be established through the pre-combustion chamber 76.
  • the pre-combustion chamber 76 is essentially free of any residual gases and is substantially isolated from the main combustion chamber 36 such that a desirable level of quiescence is created therein. This is a reliable and reproducible environment for ignition.
  • the air/fuel ratio at the spark plug electrodes may be controlled through control of flow through conduit 81 to be different to that present in the main combustion chamber 36. This is essentially possible due to the flexibility of the two fluid injection means 70.
  • the conduit 81 is not provided with valve or like means to control flow of gas between combustion chamber 36 and pre-combustion chamber 76, it will be understood that such control could be employed, if desired.
  • a solenoid valve could be opened to allow gas flow to pre-combustion 76 in response, for example, to sensed engine position. Opening, or a degree of opening, of the valve or like means might also, or alternatively, be controlled in accordance with engine operating conditions.
  • a valve openable in response to pressure in the combustion chamber 36 rising above a predetermined level might be employed instead.
  • ignition could follow entry to the pre-combustion chamber 76 of compressed gases from the combustion chamber 36 which have flowed through conduit 81.
  • FIG. 9 shows a further embodiment similar to that of FIG. 6 but including a gas conduit 81.
  • the gas conduit 81 may form part of the insert 69.
  • the embodiment is the same as that described with respect to FIG. 7.
  • the spark plug 74 could be formed integral with gas conduit 81 and, if desired, a plurality of gas conduits 81 could be provided though this may be avoided with benefit of a less complex arrangement.
  • pre-combustion chamber configuration and location, and fuel ignition management described herein is particularly applicable to four stroke cycle engines but may also be used in relation to other forms of engines including two stroke cycle engines and rotary engines.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
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AUPN1186A AUPN118695A0 (en) 1995-02-16 1995-02-16 Improvements relating to internal combustion engines
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PCT/AU1996/000078 WO1996025592A1 (en) 1995-02-16 1996-02-16 Direct fuel injected internal combustion engine

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US6302337B1 (en) 2000-08-24 2001-10-16 Synerject, Llc Sealing arrangement for air assist fuel injectors
US6402057B1 (en) 2000-08-24 2002-06-11 Synerject, Llc Air assist fuel injectors and method of assembling air assist fuel injectors
US6484700B1 (en) 2000-08-24 2002-11-26 Synerject, Llc Air assist fuel injectors
US6561167B2 (en) 2001-02-16 2003-05-13 Synerject, Llc Air assist fuel injectors
US6564770B1 (en) * 1997-12-03 2003-05-20 Orbital Engine Company (Australia) Pty. Limited Method of injection of a fuel-gas mixture to an engine
US6606973B2 (en) 2001-05-23 2003-08-19 Cordell R. Moe Rotary engine
US20050172929A1 (en) * 2004-02-09 2005-08-11 Sebastian Strauss Dual zone combustion chamber
US20110005478A1 (en) * 2008-03-12 2011-01-13 Cameron International Corporation Pre-chamber
US9476347B2 (en) 2010-11-23 2016-10-25 Woodward, Inc. Controlled spark ignited flame kernel flow in fuel-fed prechambers
US20170122184A1 (en) * 2015-10-29 2017-05-04 Woodward, Inc. Gaseous Fuel Combustion
US9653886B2 (en) 2015-03-20 2017-05-16 Woodward, Inc. Cap shielded ignition system
CN106762127A (zh) * 2017-02-09 2017-05-31 天津内燃机研究所（天津摩托车技术中心） 二冲程缸内直喷发动机
US9677459B2 (en) 2008-03-12 2017-06-13 Ge Oil & Gas Compression Systems, Llc Internal combustion engine with shrouded injection valve and precombustion chamber system
US9765682B2 (en) 2013-06-10 2017-09-19 Woodward, Inc. Multi-chamber igniter
US9803536B2 (en) 2013-11-13 2017-10-31 Denso Corporation Auxiliary chamber type internal combustion engine
US9840963B2 (en) 2015-03-20 2017-12-12 Woodward, Inc. Parallel prechamber ignition system
US9856848B2 (en) 2013-01-08 2018-01-02 Woodward, Inc. Quiescent chamber hot gas igniter
US9893497B2 (en) 2010-11-23 2018-02-13 Woodward, Inc. Controlled spark ignited flame kernel flow
US10337397B2 (en) 2017-06-14 2019-07-02 Ford Global Technologies, Llc Pre-chamber ignition system
US10815871B2 (en) * 2017-02-06 2020-10-27 Cummins Inc. Engine system for emission reduction without aftertreatment
US10833485B2 (en) 2018-12-06 2020-11-10 Federal-Mogul Ignition Gmbh Pre-chamber spark plug
CN113464267A (zh) * 2021-06-29 2021-10-01 吉林大学 一种共轨式预燃室射流点火系统
US11415041B2 (en) 2019-09-16 2022-08-16 Woodward, Inc. Flame triggered and controlled volumetric ignition
US11674494B2 (en) 2010-11-23 2023-06-13 Woodward, Inc. Pre-chamber spark plug with tubular electrode and method of manufacturing same
EP4368821A1 (en) * 2022-11-10 2024-05-15 Toyota Jidosha Kabushiki Kaisha Hydrogen engine

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EP3865690B1 (en) * 2020-02-17 2022-07-20 Wärtsilä Finland Oy A method of controlling a gas fueled reciprocating internal combustion piston engine provided with a precombustion chamber and the engine thereof
US11519322B1 (en) * 2021-08-27 2022-12-06 Caterpillar Inc. Method and system for fuel combustion
IT202200014824A1 (it) * 2022-07-14 2024-01-14 Punch Hydrocells S R L Motore a combustione interna a iniezione diretta di idrogeno

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US6564770B1 (en) * 1997-12-03 2003-05-20 Orbital Engine Company (Australia) Pty. Limited Method of injection of a fuel-gas mixture to an engine
US6302337B1 (en) 2000-08-24 2001-10-16 Synerject, Llc Sealing arrangement for air assist fuel injectors
US6402057B1 (en) 2000-08-24 2002-06-11 Synerject, Llc Air assist fuel injectors and method of assembling air assist fuel injectors
US6484700B1 (en) 2000-08-24 2002-11-26 Synerject, Llc Air assist fuel injectors
US6568080B2 (en) 2000-08-24 2003-05-27 Synerject, Llc Air assist fuel injectors and method of assembling air assist fuel injectors
US6561167B2 (en) 2001-02-16 2003-05-13 Synerject, Llc Air assist fuel injectors
US6606973B2 (en) 2001-05-23 2003-08-19 Cordell R. Moe Rotary engine
US20050172929A1 (en) * 2004-02-09 2005-08-11 Sebastian Strauss Dual zone combustion chamber
US6945219B2 (en) * 2004-02-09 2005-09-20 Bombardier Recreational Products Inc. Dual zone combustion chamber
US9745891B2 (en) 2008-03-12 2017-08-29 Ge Oil & Gas Compression Systems, Llc Internal combustion engine with shrouded injection valve and precombustion chamber system
US20140053799A1 (en) * 2008-03-12 2014-02-27 Cameron International Corporation Pre-chamber
US9222402B2 (en) 2008-03-12 2015-12-29 Ge Oil & Gas Compression Systems, Llc Pre-chamber
US9316143B2 (en) * 2008-03-12 2016-04-19 Ge Oil & Gas Compression Systems, Llc Pre-chamber
US8544443B2 (en) * 2008-03-12 2013-10-01 Cameron International Corporation Pre-chamber
US9670827B2 (en) 2008-03-12 2017-06-06 Ge Oil & Gas Compression Systems, Llc Pre-chamber
US9677459B2 (en) 2008-03-12 2017-06-13 Ge Oil & Gas Compression Systems, Llc Internal combustion engine with shrouded injection valve and precombustion chamber system
US20110005478A1 (en) * 2008-03-12 2011-01-13 Cameron International Corporation Pre-chamber
US10907532B2 (en) 2010-11-23 2021-02-02 Woodward. Inc. Controlled spark ignited flame kernel flow in fuel-fed prechambers
US9476347B2 (en) 2010-11-23 2016-10-25 Woodward, Inc. Controlled spark ignited flame kernel flow in fuel-fed prechambers
US11674494B2 (en) 2010-11-23 2023-06-13 Woodward, Inc. Pre-chamber spark plug with tubular electrode and method of manufacturing same
US9893497B2 (en) 2010-11-23 2018-02-13 Woodward, Inc. Controlled spark ignited flame kernel flow
US9856848B2 (en) 2013-01-08 2018-01-02 Woodward, Inc. Quiescent chamber hot gas igniter
US10054102B2 (en) 2013-01-08 2018-08-21 Woodward, Inc. Quiescent chamber hot gas igniter
US9765682B2 (en) 2013-06-10 2017-09-19 Woodward, Inc. Multi-chamber igniter
US9803536B2 (en) 2013-11-13 2017-10-31 Denso Corporation Auxiliary chamber type internal combustion engine
US9840963B2 (en) 2015-03-20 2017-12-12 Woodward, Inc. Parallel prechamber ignition system
US9843165B2 (en) 2015-03-20 2017-12-12 Woodward, Inc. Cap shielded ignition system
US9653886B2 (en) 2015-03-20 2017-05-16 Woodward, Inc. Cap shielded ignition system
US9890689B2 (en) * 2015-10-29 2018-02-13 Woodward, Inc. Gaseous fuel combustion
US20170122184A1 (en) * 2015-10-29 2017-05-04 Woodward, Inc. Gaseous Fuel Combustion
US10815871B2 (en) * 2017-02-06 2020-10-27 Cummins Inc. Engine system for emission reduction without aftertreatment
US11293339B2 (en) 2017-02-06 2022-04-05 Cummins Inc. Engine system for emission reduction without aftertreatment
CN106762127A (zh) * 2017-02-09 2017-05-31 天津内燃机研究所（天津摩托车技术中心） 二冲程缸内直喷发动机
US10337397B2 (en) 2017-06-14 2019-07-02 Ford Global Technologies, Llc Pre-chamber ignition system
US10833485B2 (en) 2018-12-06 2020-11-10 Federal-Mogul Ignition Gmbh Pre-chamber spark plug
US11415041B2 (en) 2019-09-16 2022-08-16 Woodward, Inc. Flame triggered and controlled volumetric ignition
US11965455B2 (en) 2019-09-16 2024-04-23 Woodward, Inc. Flame triggered and controlled volumetric ignition
CN113464267A (zh) * 2021-06-29 2021-10-01 吉林大学 一种共轨式预燃室射流点火系统
EP4368821A1 (en) * 2022-11-10 2024-05-15 Toyota Jidosha Kabushiki Kaisha Hydrogen engine
US12037964B2 (en) 2022-11-10 2024-07-16 Toyota Jidosha Kabushiki Kaisha Hydrogen engine

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ZA961254B (en) 1996-08-27
DE69628638D1 (de) 2003-07-17
AUPN118695A0 (en) 1995-03-09
KR19980702310A (ko) 1998-07-15
AR000963A1 (es) 1997-08-27
MY132217A (en) 2007-09-28
WO1996025592A1 (en) 1996-08-22
DE69628638T2 (de) 2004-05-13
EP0809753B1 (en) 2003-06-11
JPH11500510A (ja) 1999-01-12
EP0809753A4 (en) 1998-12-23
EP0809753A1 (en) 1997-12-03
TW339392B (en) 1998-09-01

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